JP2013185535A - Cooling apparatus of internal combustion engine for vehicle - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a cooling apparatus of an internal combustion engine for a vehicle which warms up the internal combustion engine and a vehicle auxiliary machine at an early time in the cooling apparatus of the internal combustion engine.SOLUTION: A control means (14) includes: a target temperature setting means (21) which sets a target temperature (γ) of a coolant in accordance with the temperature state of an internal combustion engine (2); a feedback control means (22) which controls a control valve (10) so that a coolant comes to the target temperature (γ); and a short circuit control means (23) which, when the internal combustion engine (2) is in the cold state, sets the target temperature (γ) to a warm-up temperature (α) higher than a feedback control temperature (A or B) set by the target temperature setting means (21) upon feedback control, and until reaching the warm-up temperature (α), controls the control valve (10) so that the coolant flow rate of a third coolant passage (9) becomes larger than the coolant flow rate of a first coolant passage (6) and the coolant flow rate of a second coolant passage (8).

Description

  The present invention relates to a cooling device for an internal combustion engine for a vehicle, and more particularly to a cooling device for an internal combustion engine for a vehicle that can control a refrigerant passage of a refrigerant (cooling water) of the internal combustion engine and keep the temperature of the internal combustion engine at an appropriate level.

In a cooling apparatus for an internal combustion engine mounted on a vehicle, a control valve that is electronically controlled instead of a thermostat is disposed in a refrigerant passage through which refrigerant (cooling water) flows, thereby controlling the refrigerant passage and increasing the temperature of the refrigerant. Some have improved fuel efficiency through promotion.
Control of the refrigerant temperature by the control valve is performed in order to avoid knocking when the refrigerant is heated to a high temperature (for example, 110 ° C.) as soon as possible from the cold state of the internal combustion engine and the refrigerant reaches a high temperature. The control valve is immediately controlled at a slightly lower temperature (for example, 90 ° C.).
Conventionally, as a cooling device, a minimum circulation path is provided separately from the refrigerant path, and all the control valves (switching valves) are closed at the start of warm-up of the internal combustion engine so that the refrigerant flows through the minimum circulation path. Some have warmed up the internal combustion engine early.

JP 2011-220156 A

  A control device for a cooling system according to Patent Document 1 includes a radiator that cools a refrigerant (cooling water) inside an internal combustion engine, a heat exchanger for air conditioning, and an internal combustion engine auxiliary machine (throttle body). A path is provided to connect to the internal combustion engine, a control valve (switching valve) is provided in each of these refrigerant paths, and these control valves (switching valves) are sequentially opened according to the refrigerant temperature. Specifically, when the refrigerant temperature reaches a predetermined set temperature, it is determined that the internal combustion engine has been warmed up, the radiator side refrigerant passage, the air conditioning heat exchanger side refrigerant passage, the internal combustion engine auxiliary device side Opening control is performed in the order of the refrigerant passages.

However, in an internal combustion engine cooling device, in order to improve fuel efficiency, it is important to promote the temperature rise of the operating oil of the internal combustion engine using the temperature rise of the refrigerant temperature to reduce engine friction. When the control valve is controlled only by the refrigerant temperature, in order to reliably avoid the occurrence of knocking, the hydraulic oil is controlled at a slightly lower refrigerant temperature, for example, 90 ° C. before the hydraulic oil is sufficiently warmed. The fuel consumption in the cold state could not be improved sufficiently.
Moreover, as described in Patent Document 1 described above, it is preferable that the internal combustion engine auxiliary machine and the air conditioning heat exchanger as the vehicle auxiliary machine are always maintained at an appropriate temperature. For example, when the internal combustion engine accessory is a throttle body, the oxygen amount of the air passing through the throttle body can be stabilized by keeping this temperature constant, and the air conditioner heat exchanger always operates heating. It can be maintained in a possible state. That is, when the internal combustion engine auxiliary equipment and the heat exchanger for air conditioning are in a cold state, it is preferable to warm them up as early as possible and keep them in a suitable state.
Furthermore, although the control device of Patent Document 1 warms up the internal combustion engine auxiliary machine and the air conditioner heat exchanger, there is still room for improvement in terms of warming them up early. It was.

  SUMMARY OF THE INVENTION Accordingly, an object of the present invention is to provide a cooling apparatus for a vehicle internal combustion engine that can warm up the internal combustion engine and the vehicle auxiliary equipment at an early stage.

  The present invention provides a vehicle provided with an internal combustion engine used for traveling of the vehicle, provided with a cooling device for cooling a refrigerant used for cooling the internal combustion engine, and provided with control means for controlling the refrigerant passage according to the temperature state of the internal combustion engine. In the internal combustion engine cooling apparatus, a first refrigerant passage is provided through which the refrigerant discharged from the internal combustion engine recirculates to the internal combustion engine via the cooling device, and the refrigerant discharged from the internal combustion engine passes through a vehicle accessory. And a third refrigerant passage that recirculates to the internal combustion engine and recirculates the refrigerant discharged from the internal combustion engine to the internal combustion engine and has a smaller cooling capacity than the first refrigerant passage and the second refrigerant passage. And at least one control valve for changing the flow rate of the refrigerant in the first refrigerant passage, the second refrigerant passage, and the third refrigerant passage, and the control means cools in accordance with the temperature state of the internal combustion engine. Target temperature setting means for setting the target temperature, feedback control means for controlling the control valve so that the refrigerant reaches the target temperature, and when the internal combustion engine is in a cold state, the target temperature setting means The target temperature is set to a warm-up temperature higher than the feedback control temperature set at the time of the feedback control, and the first temperature is higher than the coolant flow rate in the first refrigerant passage and the refrigerant flow rate in the second refrigerant passage until the warm-up temperature is reached. Short circuit control means for controlling the control valve so as to increase the refrigerant flow rate of the three refrigerant passages.

  The present invention can warm up the internal combustion engine and the vehicle auxiliary machine at an early stage.

FIG. 1 is a system configuration diagram of a cooling device for an internal combustion engine. (Example) FIG. 2A is a diagram illustrating an operation state of the control valve during the short-circuit control. FIG. 2B is a diagram illustrating an operation state of the control valve during auxiliary machine warm-up control. FIG. 2C is a diagram illustrating an operation state of the control valve during the cooling control. (Example) FIG. 3 is a main flowchart of control according to the embodiment. (Example) FIG. 4 is a flowchart of the short circuit control. (Example) FIG. 5 is a flowchart of auxiliary machine warm-up control. (Example) FIG. 6 is a flowchart of the first calculation method of the intermediate temperature (β). (Example) FIG. 7 is a flowchart of the second calculation method of the intermediate temperature (β). (Example) FIG. 8 is a diagram for explaining the outside air temperature and the ratio value in the calculation of the intermediate temperature (β) in FIG. 7. (Example) FIG. 9 is a flowchart of the third calculation method of the intermediate temperature (β). (Example) FIG. 10 is a diagram for determining the estimated cooling temperature with respect to the outside air temperature by calculating the intermediate temperature (β) in FIG. 9. (Example) FIG. 11 is a flowchart of the third calculation method of the intermediate temperature (β). (Example) FIG. 12 is a diagram for explaining the outside air temperature and the ratio value by calculating the intermediate temperature (β) in FIG. 11. (Example) FIG. 13 is a flowchart of cooling control. (Example) FIG. 14 is a flowchart of feedback control. (Example) FIG. 15 is a diagram showing changes in the refrigerant temperature. (Example) FIG. 16 is a system configuration diagram of a cooling device for cooling the electric motor. (Modification)

  The purpose of this invention is to quickly warm up the internal combustion engine and the vehicle auxiliary equipment by increasing the refrigerant flow rate in the third refrigerant passage having a low cooling capacity when the internal combustion engine is in a cold state and maintaining the refrigerant in a high temperature state. It is realized.

1 to 15 show an embodiment of the present invention.
In FIG. 1, reference numeral 1 denotes a power unit mounted on a vehicle.
The power unit 1 is configured by integrating an internal combustion engine 2 as a power source used for traveling of a vehicle and a transmission 3 connected to the internal combustion engine 2.
The internal combustion engine 2 is provided with a cooling device 4. The cooling device 4 includes a cooling device (radiator) 5 for cooling a refrigerant (cooling water) used for cooling the internal combustion engine 1.
Further, the cooling device 4 is provided with a first refrigerant passage 6 through which the refrigerant discharged from the internal combustion engine 2 returns to the internal combustion engine 2 via the cooling device 5. The first refrigerant passage 6 has one end connected to one side portion of the internal combustion engine 2 and the other end connected to the other side portion of the internal combustion engine 2, before and after the cooling device 5 disposed in the middle. The refrigerant is divided into a first inlet-side refrigerant passage 6 </ b> A to the cooling device 5 and a first outlet-side refrigerant passage 6 </ b> B from the cooling device 5 to the internal combustion engine 2.
In the first inlet side refrigerant passage 6A and the first outlet side refrigerant passage 6B, a refrigerant discharged from the internal combustion engine 2 forms a vehicle auxiliary machine 7 so as to short-circuit the cooling device 5 (first vehicle auxiliary machine ( A second refrigerant passage 8 that recirculates to the internal combustion engine 2 via an air conditioning heat exchanger or throttle body) 7A is provided. The second refrigerant passage 8 includes a second main refrigerant passage 8A and a second branch refrigerant passage 8B branched from the second main refrigerant passage 8A and connected to the first outlet-side refrigerant passage 6B. A second vehicle auxiliary machine 7B constituting the vehicle auxiliary machine 7 is disposed in the second branch refrigerant passage 8B.

In addition, the refrigerant discharged from the internal combustion engine 2 is returned to the internal combustion engine 2 so as to short-circuit the cooling device 5 between the first inlet side refrigerant passage 6A and the first outlet side refrigerant passage 6B. A third refrigerant passage 9 having a cooling capacity smaller than that of the second refrigerant passage 8 is provided in parallel with the second refrigerant passage 8.
Furthermore, one control valve 10 is disposed in the middle of the first inlet-side refrigerant passage 6A. The control valve 10 is connected in parallel to each end of the second refrigerant passage 8 and the third refrigerant passage 9. The control valve 10 controls the first inlet-side refrigerant passage 6A, the second refrigerant passage 8, and the third refrigerant passage 9 on the downstream side of the control valve 10, and the first inlet-side refrigerant passage 6A and the second refrigerant passage. 8 and the refrigerant flow rate of the third refrigerant passage 9 is changed. The other ends of the second main refrigerant passage 8A, the second branch refrigerant passage 8B, and the third refrigerant passage 9 are connected in parallel to the first outlet-side refrigerant passage 6B.
The control valve 10 is a three-way switching valve that is electronically controlled. As shown in FIG. 2, the control valve 10 includes a case 11 and a crescent-shaped valve body 13 that rotates in an internal space 12 in the case 11. The control valve 10 communicates one end of each of the first inlet-side refrigerant passage 6A, the second refrigerant passage 8, and the third refrigerant passage 9 with the internal space 12, and the valve body 12 is rotated to move the first inlet side. The refrigerant passage 6A, the second refrigerant passage 8 and the third refrigerant passage 9 are switched to communicate with each other, and the short-circuit control is being executed (FIG. 2A) and the auxiliary machine warm-up control is being executed (FIG. 2). 2 (B)), the cooling control is being executed (FIG. 2C).
The control valve 10 communicates with the control means 14 and is electronically controlled by the control means 14.

In the first outlet-side refrigerant passage 6B, a water pump 15 is disposed on the internal combustion engine 2 side of the connection portion of each other end of the second main refrigerant passage 8A, the second branch refrigerant passage 8B, and the third refrigerant passage 9. ing.
The control means 14 includes a power source 16 for supplying electric power, an ignition switch 17 for turning on / off the internal combustion engine 2, a knocking sensor 18 for detecting abnormal combustion inside the internal combustion engine 2, and a refrigerant ( A coolant temperature sensor 19 that detects the (cooling water) temperature (Tw) and an outside air temperature sensor 20 that detects the outside air temperature communicate with each other.
The knocking sensor 18 is composed of a piezoelectric element attached to the internal combustion engine 2. The knocking sensor 18 detects vibration of the internal combustion engine 2 at a predetermined cycle, and generates electric current when receiving the vibration of the internal combustion engine 2.

The control means 14 controls the refrigerant flow rates of the refrigerant passages 6, 8, 9 according to the temperature state of the internal combustion engine 2.
Therefore, the control unit 14 includes a target temperature setting unit 21, a feedback control unit 22, a short-circuit control unit 23, an auxiliary machine warm-up control unit 24, and a cooling control unit 25.
The target temperature setting means 21 sets the target temperature (γ) of the refrigerant according to the temperature state of the internal combustion engine 2.
The feedback control means 22 controls the control valve 10 so that the refrigerant reaches the target temperature (γ) (see FIG. 14). A fail-safe valve 26 attached to the control valve 10 communicates with the feedback control means 22.
When the internal combustion engine 2 is in a cold state, the short-circuit control means 23 is a feedback control temperature (first feedback control temperature A or second feedback temperature) at which the target temperature setting means 21 sets the target temperature (γ) during feedback control. A warm-up temperature (α) higher than the feedback control temperature B) is set, and the third refrigerant is higher than the refrigerant flow rate in the first refrigerant passage 6 and the refrigerant flow rate in the second refrigerant passage 8 until the warm-up temperature (α) is reached. The control valve 10 is controlled so that the refrigerant flow rate in the passage 9 is increased (see FIGS. 2A, 4 and 15). The first feedback control temperature A and the second feedback control temperature B are in a relationship of A <B.

The auxiliary machine warm-up control means 24 warms up the vehicle auxiliary machine 7 by increasing the refrigerant flow rate in the second refrigerant passage 8 when the internal combustion engine 2 is warmed up (see FIG. 5).
Further, the auxiliary machine warm-up control means 24 controls the control valve 10 so as to maintain the open state of the third refrigerant passage 9 (see FIG. 2B).
Further, the auxiliary machine warm-up control means 24 performs cooling control until the refrigerant temperature (Tw) reaches an intermediate temperature (β) set between the warm-up temperature (α) and the feedback control temperature (A or B). Prohibited (see FIG. 5).
Furthermore, the auxiliary equipment warm-up control means 24 calculates the intermediate temperature (β) by subtracting the estimated cooling temperature estimated from the warm-up temperature (α) based on the outside air temperature (see FIGS. 9 and 10).
Further, the auxiliary machine warm-up control means 24 sets the intermediate temperature (β) to a higher temperature when abnormal combustion by the knocking sensor 18 is detected than when the abnormal combustion by the knocking sensor 18 is not detected. (See FIGS. 7, 8, 11, and 12).

The cooling control means 25 increases the refrigerant flow rate in the first refrigerant passage 6 to cool the refrigerant when the vehicle auxiliary machine 7 is warmed up (see FIG. 13).
Further, the cooling control means 25 maintains at least one of the other refrigerant passages in an open state and increases the refrigerant flow rate in the first refrigerant passage 6 when the vehicle auxiliary machine 7 is warmed up. The control valve 10 is controlled (see FIG. 2C). In this case, the other refrigerant passage is the second refrigerant passage 8.
Furthermore, the cooling control means 25 closes at least one of the refrigerant passages different from the other refrigerant passages maintained in the open state when the vehicle auxiliary equipment 7 is warmed up. The control valve 10 is controlled (see FIG. 2C). In this case, the other refrigerant passage is the third refrigerant passage 9.

A change in the refrigerant temperature (Tw) will be described.
As shown in FIG. 15, in the change of the refrigerant temperature (Tw), the third refrigerant passage is from the start of the internal combustion engine 2 (time t1) until the first fixed period T1 has elapsed (time t2). Only 9 is opened, and the refrigerant temperature (Tw) is raised to the warm-up temperature (α).
Then, after the refrigerant temperature (Tw) reaches the warm-up temperature (α), the third refrigerant passage 9 and the second refrigerant passage 8 are opened, the heat of the refrigerant is taken away, and the refrigerant temperature (Tw) is reduced. It decreases to the intermediate temperature (β) in the second constant period T2 (time t3).
In the second fixed period T2, the cooling device 5 and the vehicle auxiliary machine 7 are in a cold state until the refrigerant flows, so that the gradient becomes steep at the first circulation of the refrigerant.
Thereafter, when the cooling device 5 and the vehicle auxiliary device 7 are gradually warmed up, the gradient becomes gentle, that is, the fan and the heat exchanger of the cooling device 5 do not change the rotation speed of the attached fan. As long as a constant cooling capacity is maintained. That is, this cooling capacity changes with the quadratic curve R so as not to gradually cool.
Then, when the refrigerant temperature (Tw) becomes lower than the intermediate temperature (β), the auxiliary machine warm-up control is executed, the first refrigerant passage 6 and the second refrigerant passage 8 are opened, and the feedback control temperature (A or B). When the third fixed period T3 elapses until () is reached (time t4), feedback control is started.
In this feedback control temperature, as described above, there are the first feedback control temperature A and the second feedback control temperature B. In the broken line M, knocking is detected and the target temperature (γ) is controlled by feedback control. The change of the refrigerant | coolant temperature (Tw) at the time of setting to temperature (A) is shown.
On the other hand, when there is knocking, the intermediate temperature (β) is set not to be higher than in the case without knocking, so that the cooling control is executed faster.

Next, control according to this embodiment will be described.
As shown in the main flowchart of FIG. 3, when the program of the control means 14 is started (step A01), first, it is determined whether or not the power supply 16 is turned on, so-called accessory power supply is turned on (step A02). If step A02 is NO, this determination is continued.
When step A02 is YES, short circuit control is performed (step A03). The short-circuit control in step A03 will be specifically described with reference to the flowchart of FIG.
After this short-circuit control, auxiliary machine warm-up control is performed (step A04). The auxiliary machine warm-up control in step A04 will be specifically described with reference to the flowchart of FIG.
After this auxiliary machine warm-up control, cooling control is performed (step A05). The cooling control in step A05 will be specifically described with reference to the flowchart of FIG.
After this cooling control, feedback control is performed (step A06). The feedback control in step A06 will be specifically described with reference to the flowchart of FIG.
After this feedback control, the program is ended (step A07).

The short circuit control in step A03 of FIG. 3 is performed according to the flowchart of FIG.
This short-circuit control is a case where the temperature of the internal combustion engine 2 has not reached the preset warm-up temperature (α), and it is determined that the internal combustion engine 2 is in the cold state. Therefore, the control valve 10 is controlled. (Refer to FIG. 2 (A)), the passage area of the first refrigerant passage 6 and the second refrigerant passage 8 is reduced, or the first refrigerant passage 6 and the second refrigerant passage 8 are closed, so that the third refrigerant passage The refrigerant flow rate of 9 is made larger than the refrigerant flow rates of the first refrigerant passage 6 and the second refrigerant passage 8 to warm up the internal combustion engine 2 at an early stage.
As shown in FIG. 4, when the program of the short-circuit control means 23 starts (step B01), first, the refrigerant temperature (Tw) is acquired from the refrigerant temperature sensor 19 (step B02), and the refrigerant temperature (Tw) is It is determined whether or not the temperature is equal to or higher than a preset warm-up temperature (α) (Tw ≧ α) (step B03). In step B03, the target temperature setting unit 21 sets the target temperature (γ) of the refrigerant according to factors such as the refrigerant temperature (Tw).
When this step B03 is NO, the control valve 10 is controlled (see FIG. 2A), and the refrigerant flow rate in the third refrigerant passage 9 is set to be higher than the refrigerant flow rates in the first refrigerant passage 6 and the second refrigerant passage 8. Increase (step B04). Thereby, the internal combustion engine 2 can be warmed up early.
After step B04, the process returns to step B02.
If step B03 is YES, knocking determination processing is performed by the knocking sensor 18 (step B05).
Then, it is determined whether or not there is knocking (step B06). In step B06, when the knocking sensor 18 detects the generated current and the vibration of the internal combustion engine 2 is equal to or greater than a predetermined value, it is determined that knocking is present. In addition, the knocking determination is periodically repeated. If it is detected that knocking has occurred even once during a predetermined period, it is determined that knocking is present. On the other hand, if knocking is not detected during the predetermined period, there is no knocking. Judge.
If step B06 is YES, the target temperature (γ) is set to the first feedback control temperature (A) (see FIG. 15) (step B07).
On the other hand, if step B06 is NO, the target temperature (γ) is set to the second feedback control temperature (B) (step B08).
After the process of step B07 or after the process of step B08, the program is ended (step B09).

The auxiliary machine warm-up control in step A04 of FIG. 3 is performed according to the flowchart of FIG.
This auxiliary machine warm-up control is executed after the internal combustion engine 2 is warmed up by the short-circuit control, and warms up the vehicle auxiliary machine 7 quickly and efficiently. Specifically, the intermediate temperature (β) is calculated based on the warm-up temperature (α) and the target temperature (γ), and the second refrigerant passage 8 is used until the refrigerant temperature (Tw) reaches the intermediate temperature (β). The control valve 10 is controlled so as to increase the refrigerant flow rate (see FIG. 2B), and the vehicle auxiliary machine 7 is warmed up.
As shown in FIG. 5, when the program of the auxiliary machine warm-up control means 24 is started (step C01), first, an intermediate temperature (β) is calculated (step C02). This intermediate temperature (β) is calculated in FIGS.
Then, the control valve 10 is controlled (see FIG. 2B), and the refrigerant flow rate in the second refrigerant passage 8 is increased (step C03). Thereby, the vehicle auxiliary machine 7 can be warmed up early.
Thereafter, it is determined whether or not the refrigerant temperature Tw ≦ the intermediate temperature β (step C04). If this step C04 is NO, the process returns to step C02 so as to prohibit the cooling control.
On the other hand, if this step C04 is YES, the program is ended (step C05).

As the calculation method of the intermediate temperature (β) in step C02, there are the following first to fourth calculation methods.
(1) As a first calculation method, as shown in FIG. 6, when the program starts (step D01), the intermediate temperature β is set to
Intermediate temperature β = (warm-up temperature α + target temperature γ) × 0.5 (ratio value: average value)
(Step D02).
Note that the intermediate temperature β is multiplied by 0.5 as a ratio value, but when it is determined that knocking is present, cooling is required at an early stage. It is possible to control the temperature (β) to be set to a high value so that the opening of the first refrigerant passage 6 is accelerated.
Then, the program is ended (step D03).
(2) In the second calculation method, as shown in FIGS. 7 and 8, in consideration of the presence or absence of knocking, when knocking is present, the first set value (C) is set and the ratio value is set to 0. On the other hand, if there is no knocking, the second set value (D) is set and the ratio value is set to 0.5. Here, the first set value (C) and the second set value (D) have a relationship of C <D.
Then, as shown in FIG. 7, when the program is started (step E01), it is determined whether or not the target temperature (γ) is the first set value (C: set value on the lower side) (step E02).
If this step E02 is YES, the intermediate temperature (β) is
Intermediate temperature β = (warm-up temperature α + target temperature γ) × 0.8
(Step E03).
On the other hand, if this step E02 is NO, the intermediate temperature (β) is
Intermediate temperature β = (warm-up temperature α + target temperature γ) × 0.5
(Step E04).
After the process of step E03 or after the process of step E04, the program is ended (step E05).
(3) As a third calculation method, as shown in FIGS. 9 and 10, an estimated cooling temperature is obtained with respect to the outside air temperature detected from the outside air temperature sensor 20.
For this reason, a table for determining the estimated cooling temperature according to the outside air temperature is set in FIG.
As shown in FIG. 9, when the program starts (step F01), the outside air temperature from the outside air temperature sensor 20 is detected, and the estimated cooling temperature is estimated based on the detected outside air temperature as shown in FIG. (Step F02).
And the intermediate temperature (β)
Intermediate temperature β = warm-up temperature α−estimated cooling temperature is calculated (step F03).
Thereafter, the program is ended (step F04).
(4) In the fourth calculation method, as shown in FIGS. 11 and 12, in consideration of the presence or absence of knocking, when knocking is present, the first set value (C) is set and the ratio value is set to 0. On the other hand, if there is no knocking, the second set value (D) is set and the ratio value is set to 0.5. Here, there is a relationship of the first set value C <the second set value D.
Further, as shown in FIG. 10 described above, an estimated cooling temperature is obtained for the outside air temperature detected from the outside air temperature sensor 20.
As shown in FIG. 11, when the program starts (step G01), the outside air temperature from the outside air temperature sensor 20 is detected, and the estimated cooling temperature is estimated based on the detected outside air temperature as shown in FIG. (Step G02).
And the intermediate temperature (β)
Intermediate temperature β = warm-up temperature α−estimated cooling temperature is calculated (step G03).
Then, it is determined whether or not the target temperature (γ) is the first set value (C: the set value on the lower side) (step G04).
If this step G04 is YES, the intermediate temperature (β) is
Intermediate temperature β = (warm-up temperature α + target temperature γ) × 0.8
(Step G05).
On the other hand, if this step G04 is NO, the intermediate temperature (β) is
Intermediate temperature β = (warm-up temperature α + target temperature γ) × 0.5
(Step G06).
After the process of step G05 or after the process of step G06, the program is ended (step G07).

The cooling control in step A05 in FIG. 3 is performed according to the flowchart in FIG.
This cooling control is executed after the vehicle auxiliary machine 7 is warmed up by the auxiliary machine warm-up control, and after the vehicle auxiliary machine 7 is warmed up, the refrigerant temperature (Tw) is quickly set to the target temperature. Control to (γ). Specifically, when the warm-up of the vehicle auxiliary machine 7 is completed, the control valve 10 is controlled (see FIG. 2C), the refrigerant flow rate to the first refrigerant passage 6 is increased, and the cooling device (radiator) 5 At the same time, the third refrigerant passage 9 is closed, the passage water pressure is increased, and the refrigerant flow rate per unit time flowing to the cooling device 5 is increased. Furthermore, since the second refrigerant passage 8 is maintained in an open state, the temperature of the vehicle auxiliary machine 7 can be maintained even during the cooling control.
The feature of this cooling control is that it is performed after the auxiliary machine warm-up control. When the auxiliary machine warm-up control is completed, the temperature of the vehicle auxiliary machine 7 is equal to or higher than a certain level, so that the second refrigerant passage 8 is used as a short-circuit passage in the same manner as the third refrigerant passage 9.
Thereby, even if the cooling by the cooling device 5 is started, it becomes difficult to cause rapid cooling. Moreover, since the second refrigerant passage 8 is used, the vehicle auxiliary machine 7 can be kept at a stable temperature.
As shown in FIG. 13, when the program is started (step H01), the control valve 10 is controlled (see FIG. 2C) to increase the refrigerant flow rate in the first refrigerant passage 6 while the third refrigerant passage 9 is Close (step H02).
Then, it is determined whether or not the refrigerant temperature Tw ≦ the target temperature γ (step H03). When the step H03 is NO, the process returns to the step H02. On the other hand, when the step H03 is YES, the program is executed. End (step H04).

Next, the feedback control in step A06 of FIG. 3 is performed according to the flowchart of FIG.
This feedback control controls the control valve 10 in order to keep the refrigerant temperature (Tw) at the target temperature (γ). When the refrigerant temperature (Tw) is equal to or higher than the abnormal heating temperature (Ts), the control valve 10 It is determined that an abnormality has occurred and the cooling is not performed, and the fail-safe valve 26 is opened.
As shown in FIG. 14, when the program starts (step I01), it is determined whether or not the refrigerant temperature Tw> the target temperature γ (step I02).
If this step I02 is YES, the control valve 10 is controlled to close the first refrigerant passage 6 by a predetermined angle (step I03). That is, the passage opening area of the first refrigerant passage 6 is set to the small side.
On the other hand, when this step I03 is NO, the control valve 10 is controlled to open the first refrigerant passage 6 by a predetermined angle (step I04). That is, the passage opening area of the first refrigerant passage 6 is set to the larger side.
After the process of step I03 or after the process of step I04, it is determined whether or not the refrigerant temperature Tw ≧ the abnormal heating temperature Ts (step I05).
If this step I05 is YES, the fail safe valve 26 is opened (step I06), and the process returns to the step I02.
If this step I05 is NO, it is determined whether or not the ignition switch 17 is off (step I07).
If step I07 is NO, the process returns to step I02.
If this step I07 is YES, the target temperature (γ) is reset (step I08), and the program is ended (step I09).

Although the embodiments of the present invention have been described above, the configuration of the above-described embodiments will be described for each claim.
First, in the invention according to claim 1, a first refrigerant passage 6 is provided in which the refrigerant discharged from the internal combustion engine 2 recirculates to the internal combustion engine 2 through the cooling device 5, and the refrigerant discharged from the internal combustion engine 2 is the vehicle auxiliary machine 7. And a second refrigerant passage 8 that recirculates to the internal combustion engine 2 through the refrigerant, and a refrigerant discharged from the internal combustion engine 2 is recirculated to the internal combustion engine 2 and has a cooling capacity smaller than that of the first refrigerant passage 6 and the second refrigerant passage 8. The refrigerant passage 9 is provided, and at least one control valve 10 that changes the refrigerant flow rates of the first refrigerant passage 6, the second refrigerant passage 8, and the third refrigerant passage 9 is provided. The control means 10 includes a target temperature setting means 21 that sets a target temperature (γ) of the refrigerant according to the temperature state of the internal combustion engine 2 and a feedback control means that controls the control valve 10 so that the refrigerant reaches the target temperature. 22 and when the internal combustion engine 2 is in a cold state, the target temperature setting means 21 has a warm-up temperature (α) higher than the feedback control temperature (A or B) that sets the target temperature (γ) during the feedback control. The control valve 10 is set so that the refrigerant flow rate in the third refrigerant passage 9 is larger than the refrigerant flow rate in the first refrigerant passage 6 and the refrigerant flow rate in the second refrigerant passage 8 until the warm-up temperature (α) is reached. Short circuit control means 23 for controlling.
As a result, when the internal combustion engine 2 is in a cold state, the refrigerant flow rate in the third refrigerant passage 9 having a low cooling capacity is increased so that the refrigerant is easily maintained in a high temperature state. With this configuration, the target temperature setting means 21 can set the warm-up temperature (α) higher than the feedback control temperature (A or B) set during the feedback control as the target temperature (γ). The internal combustion engine 2 can be warmed up early.
In the invention according to claim 2, the control means 14 increases the refrigerant flow rate in the second refrigerant passage 8 to warm up the vehicle auxiliary machine 7 when the internal combustion engine 2 is warmed up. Means 24 and cooling control means 25 for cooling the refrigerant by increasing the refrigerant flow rate in the first refrigerant passage 6 when the vehicle auxiliary machine 7 is warmed up.
With such a configuration, after the internal combustion engine 2 is warmed up, the refrigerant heated by the short-circuit control means 23 is flowed to the vehicle auxiliary machine 7 before increasing the refrigerant flow rate to the cooling device 5. Therefore, the warming-up of the vehicle auxiliary machine 7 can be started earlier than before, and at this time, since the refrigerant temperature (Tw) has reached the warm-up temperature (α), it is caused by the high refrigerant temperature (Tw). Can warm up quickly. Furthermore, when the vehicle auxiliary machine 7 is warmed up, since the refrigerant is after the heat has been taken away by the vehicle auxiliary machine 7, the refrigerant temperature (Tw) becomes close to the feedback control temperature (A or B). If the control of the cooling control means 25 is started after the vehicle auxiliary machine 7 is warmed up, the feedback control can be started in a short time.
In the invention according to claim 3, the auxiliary machine warm-up control means 24 controls the control valve 10 so as to maintain the open state of the third refrigerant passage 9.
With such a configuration, when the cooling device 5 of the internal combustion engine 2 according to claim 2 increases the refrigerant flow rate in the second refrigerant passage 8 to warm up the vehicle auxiliary machine 7, the third refrigerant passage 9 Since the open state is maintained, a part of the refrigerant flowing through the internal combustion engine 2 is recirculated to the internal combustion engine 2 through the third refrigerant passage 9. Therefore, even if heat is used to warm up the vehicle auxiliary machine 7, the refrigerant is heated at the same time in the third refrigerant passage 9, and therefore, the high temperature refrigerant is always supplied to the vehicle auxiliary machine 7. The vehicle auxiliary machine 7 can be warmed up early. When the outside air temperature is low, the refrigerant temperature (Tw) may be lower than the feedback control temperature (A or B) when the refrigerant is circulated through the vehicle auxiliary machine 7. For this reason, it is also effective in preventing rapid cooling.
In the invention according to claim 4, the auxiliary machine warm-up control means 24 is the intermediate temperature (β) in which the refrigerant temperature (Tw) is set between the warm-up temperature (α) and the feedback control temperature (A or B). Cooling control is prohibited until the value is reached.
Generally, if the cooling control is executed immediately after the auxiliary machine warm-up control is executed, the cooling by the cooling device 5 is started before the vehicle auxiliary machine 7 is warmed up. At this time, since the refrigerant is deprived of heat from both the vehicle auxiliary machine 7 and the cooling device 5, there is a risk of rapid cooling. Therefore, with the above-described configuration, the vehicle auxiliary machine 7 can be warmed up until the refrigerant reaches the intermediate temperature (β), that is, the state in which the refrigerant is cooled by the vehicle auxiliary machine 7 can be maintained. Rapid cooling can be prevented.
In the invention according to claim 5, the auxiliary machine warm-up control means 24 calculates the intermediate temperature (β) by subtracting the estimated cooling temperature estimated from the warm-up temperature (α) by the outside air temperature.
With such a configuration, since the control of the vehicle auxiliary machine 7 can be maintained until the vehicle auxiliary machine 7 is completely warmed up, the vehicle auxiliary machine 7 can be warmed up early. Moreover, when cooling control is performed after control of the vehicle auxiliary machine 7, the temperature fall of the vehicle auxiliary machine 7 can be suppressed.
In the invention according to claim 6, the internal combustion engine 2 is provided with a knocking sensor 18 that detects internal abnormal combustion. Further, the auxiliary machine warm-up control means 24 sets the intermediate temperature (β) to a higher temperature when abnormal combustion by the knocking sensor 18 is detected than when the abnormal combustion by the knocking sensor 18 is not detected. .
Generally, when abnormal combustion occurs in the internal combustion engine 2, it is necessary to cool early in order to eliminate the abnormal combustion. Thus, with the above configuration, when abnormal combustion is detected, the intermediate temperature (β) is set to a high temperature, so that the start timing of the cooling control can be advanced and early cooling can be achieved.
In the invention according to claim 7, the cooling control means 25 maintains at least one of the other refrigerant passages in an open state when the vehicle auxiliary machine 7 is warmed up, and the refrigerant in the first refrigerant passage 6. The control valve 10 is controlled so as to increase the flow rate.
Generally, the cooling device 5 is used to cool the refrigerant flowing through the first refrigerant passage 6. However, if the cooling device 5 itself is in a cold state, the refrigerant is suddenly cooled when the refrigerant flows in for the first time, and may be overcooled. Therefore, with the above-described configuration, the open state of the other refrigerant passages is maintained at the first inflow of the cooling device 5, so that rapid cooling can be mitigated and overcooling can be prevented. That is, the cooling control means 25 controls the control valve 10 to cool a part of the refrigerant so that the third refrigerant passage 9 having a low cooling capacity and the second refrigerant passage 8 after warm-up are used as a short-circuit passage. Instead, the refrigerant is recirculated to the internal combustion engine 2 to prevent the refrigerant from being overcooled.
In the invention according to claim 8, the other refrigerant passage in claim 7 is the second refrigerant passage 8.
With such a configuration, the vehicle auxiliary machine 7 can be kept at a constant temperature during the control, which is preferable when the vehicle travels.
In the invention according to claim 9, the cooling control means 25 closes at least one of the refrigerant passages different from the other refrigerant passages maintained in the open state when the vehicle auxiliary equipment 7 is warmed up. The control valve 10 is controlled so as to be in a state.
With such a configuration, by closing at least one of the other cooling passages at the first inflow to the cooling device 5, the pressure in the first refrigerant passage 6 can be increased to increase the flow rate of the refrigerant, The refrigerant flow rate per time passing through the cooling device 5 increases. For this reason, the amount of heat received from the refrigerant in the cooling device 5 increases, and the cold state is quickly eliminated.
In the invention according to claim 10, the other refrigerant passage in claim 9 is the third refrigerant passage 9.
With such a configuration, the efficiency of the cooling control can be improved by closing the third refrigerant passage 9.

In the present invention, the cooling device 4 can be configured as follows.
For example, as a modification, as shown in FIG. 16, in the cooling device 4 according to the above embodiment, the internal combustion engine 2 can be used as a power source so that it can be used for an electric vehicle such as a hybrid vehicle or an electric vehicle. In addition, the electric motor 27 is a cooling target. Specifically, in the electric motor 27, a hole is formed in a resin motor case that covers a coil that is a heating element, and the hole is used as a refrigerant passage through a metal tube, or the motor case is made of metal. It is also possible to integrally form the refrigerant passage. In the case of an electric vehicle, since the internal combustion engine 2 is not provided and there is no throttle body, only the first vehicle auxiliary machine 7A of the second main refrigerant passage is arranged as the vehicle auxiliary machine 7.
Thus, even with the configuration in which the electric motor is mounted on the vehicle, the same effects as those of the above-described embodiment can be obtained.

  Further, in order to detect the occurrence timing of knocking with higher accuracy, the knocking sensor detects knocking, determines that the control for retarding the ignition timing as a countermeasure against knocking has been activated, and sets the target temperature of the control valve, for example, It is also possible to change from 110 ° C. to 90 ° C.

  The cooling device according to the present invention can be applied to various internal combustion engines.

2 Internal combustion engine 4 Cooling device 5 Cooling device 6 First catalyst passage 7 Vehicle auxiliary equipment 8 Second catalyst passage 9 Third catalyst passage 10 Control valve 14 Control means 15 Water pump 16 Power supply 17 Ignition switch 18 Knock sensor 19 Refrigerant temperature sensor 20 Outside air temperature sensor 21 Target temperature setting means 22 Feedback control means 23 Short-circuit control means 24 Auxiliary machine warm-up control means 25 Cooling control means

Claims (10)

  An internal combustion engine for a vehicle provided with an internal combustion engine used for traveling of a vehicle, provided with a cooling device for cooling a refrigerant used for cooling the internal combustion engine, and provided with control means for controlling a refrigerant passage according to the temperature state of the internal combustion engine. In the cooling device, there is provided a first refrigerant passage through which the refrigerant discharged from the internal combustion engine recirculates to the internal combustion engine via the cooling device, and the refrigerant discharged from the internal combustion engine passes through the vehicle accessory to the internal combustion engine. A second refrigerant passage that recirculates to the internal combustion engine, a refrigerant that is discharged from the internal combustion engine is recirculated to the internal combustion engine, and a third refrigerant passage that is smaller in cooling capacity than the first refrigerant passage and the second refrigerant passage is provided, At least one control valve for changing a refrigerant flow rate in the first refrigerant passage, the second refrigerant passage, and the third refrigerant passage is provided, and the control means is configured to change a target temperature of the refrigerant according to a temperature state of the internal combustion engine. Target temperature setting means for setting, feedback control means for controlling the control valve so that the refrigerant reaches the target temperature, and when the internal combustion engine is in a cold state, the target temperature setting means sets the target temperature to the target temperature. A warm-up temperature higher than the feedback control temperature set during the feedback control is set, and until the warm-up temperature is reached, the coolant flow rate in the third coolant passage is higher than the coolant flow rate in the first coolant passage and the coolant flow rate in the second coolant passage. A cooling apparatus for an internal combustion engine for a vehicle, comprising: short-circuit control means for controlling the control valve so as to increase a refrigerant flow rate.   The control means includes auxiliary machine warm-up control means for warming the vehicle auxiliary equipment by increasing the refrigerant flow rate in the second refrigerant passage when the internal combustion engine is warmed up, and the vehicle auxiliary equipment The cooling apparatus for an internal combustion engine for a vehicle according to claim 1, further comprising cooling control means for cooling the refrigerant by increasing a flow rate of the refrigerant in the first refrigerant passage when the engine is warmed up.   The cooling apparatus for an internal combustion engine for a vehicle according to claim 2, wherein the auxiliary machine warm-up control means controls the control valve so as to maintain an open state of the third refrigerant passage.   The auxiliary machine warm-up control means prohibits cooling control until the refrigerant temperature reaches an intermediate temperature set between the warm-up temperature and the feedback control temperature. A cooling apparatus for an internal combustion engine for a vehicle according to claim 1.   5. The cooling apparatus for an internal combustion engine for a vehicle according to claim 4, wherein the auxiliary machine warm-up control means calculates the intermediate temperature by subtracting the estimated cooling temperature estimated from the warm-up temperature based on the outside air temperature. .   The internal combustion engine is provided with a knocking sensor for detecting internal abnormal combustion, and the auxiliary equipment warm-up control means uses the intermediate temperature to detect abnormal combustion by the knocking sensor when abnormal combustion is detected by the knocking sensor. 6. The cooling apparatus for an internal combustion engine for a vehicle according to claim 4, wherein the temperature is set to be higher than that in a case where no is detected.   The cooling control means controls the control so as to maintain at least one of the other refrigerant passages in an open state and increase the refrigerant flow rate in the first refrigerant passage when the vehicle auxiliary equipment is warmed up. The cooling device for an internal combustion engine for a vehicle according to any one of claims 2 to 6, wherein the valve is controlled.   8. The cooling apparatus for an internal combustion engine for a vehicle according to claim 7, wherein the other refrigerant passage is the second refrigerant passage.   The cooling control means controls the control so that at least one of the refrigerant passages different from the other refrigerant passages maintained in an open state is closed when the vehicle accessory is warmed up. The cooling device for an internal combustion engine for a vehicle according to claim 7 or 8, wherein the valve is controlled.   The cooling apparatus for an internal combustion engine for a vehicle according to claim 9, wherein the another refrigerant passage is the third refrigerant passage.

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